Lower drafting rollers of spinning machines



March 1966 SHIGEMATSU TAKITA 3,240,031

LOWER DRAFTING ROLLERS 0F SPINNING MACHINES Filed Jan. 2, 1963 5 Sheets-Sheet 1 FIG. 4

INVENTOR. SHIGEMATSU TAKITA BY a H O flTTORNEY March 1966 SHIGEMATSU TAKITA 3,240,031

LOWER DRAFTING ROLLERS OF SPINNING MACHINES Filed Jan. 2, 1963 5 Sheets-Sheet 2 INVENTOR. SHIGEMATSU TAKITA flrh 2 7 ATTORNEY MaI'Ch 1966 SHIGEMATSU TAKHTA 3,240,031

LOWER DRAFTING ROLLERS OF SPINNING MACHINES Filed Jan. 2, 1965 5 Sheets-Sheet 5 INVENTOR. SHIGEMA TSU TAKITA BY z ATTORNE;

March 1966 SHIGEMATSU TAKITA 3,240,031

LOWER DRAFTING ROLLERS 0F SPINNING MACHINES Filed Jan. 2, 1963 5 Sheets-Sheet 4 /o/ /o,o Ii Z a F Li; 1 I I I P I 1 W ,4 ma

FIG. 14 INVENTOR.

SHIGEMATSU TAKITA ATTORNEY 3,240,031 LOWER DRAFTING ROLLERS OF SPINNING MACHINES Filed Jan. 2, 1963 March 15, 1966 SHIGEMATSU TAKITA 5 Sheets-Sheet 5 22 INVENTOR.

SHIGEMATSU TAKITA BY ATTORNEY;

United States Patent C 3,240,031 LOWER DRAFTING RULLERS F SPINNING MACHINES Shigematsu Takita, 186 Z-chome, Kirihata Nagaoyama, Takarazuka, Hyogo, Japan Filed Jan. 2, 1963, Ser. No. 249,017 3 Claims. (Cl. 64-9) This invention relates to spinning machines and, more particularly to the lower drafting or drawing rollers of such machines.

It is the chief object of the invention is provide a sectional lower roller which produces a more uniform and superior quality of yarn than prior art devices.

Another object is to provide a sectional lower roller which practically eliminates severance of yarn.

Yet another object is to provide a roller of the type mentioned which effects the desired results by eliminating transverse vibrations of the roller sections even although consecutive bearings may not be in precise alignment.

Still another object is to provide a roller as aforesaid which effects the desired and superior results by eliminating torsional oscillation and its inevitable concomitant, non-uniform instantaneous peripheral speeds of the several roller sections.

A further object is to provide a sectional roller wherein the sections are loosely connected in end-to-end relation for positive rotation as a unit, and, at the same time, for a slight and limited relative axial rotation as well as for relative angular movement of each section in planes through its axis of rotation, relatively to the next succeeding section.

Another object is to provide a. sectional roller as aforesaid which while effecting all of the objects aforesaid, is of indefinite life, wherein each section may be easily removed for repair or replacement without disturbing adjacent sections, and wherein the sections themselves are interconnected by sleeve means which journal the roller sections and so may be replaced or renewed as desired without replacement of the sections themselves.

Other objects and advantages inherent in my invention will become obvious to those skilled in the art, after a study of the following detailed description, in connection with the accompanying drawings.

In the drawings:

FIGURE 1 is a explanatory diagrammatic view showing (a) properly spun yarn as produced by the present invention; (b) defective yarn produced by prior art machines having lower rollers with fixed coupling; and (c) spun yarn produced at an ultra-high rate of drafting;

FIGURES 2, 3, 4, 5 and 6 are explanatory diagrammatic views showing to an exaggerated scale, conditions which may exist in spinning machines wherein the lower roller sections have a fixed or rigid coupling;

FIGURE 7 is a longitudinal axial section of a fourth modification, using a sleeve as coupler between contiguous roller sections;

FIGURE 8 is a detail section axially through an end of one roller section and showing, in addition, one mounting shaft section;

FIGURE 9 is an end view looking from the left in FIGURE 8;

FIGURE 10 is a longitudinal axial section of the coupling sleeve used in the species of FIGURE 7, etc.;

FIGURE 11 is an end view looking from the right of FIGURE 10;

FIGURE 12 is a transverse section taken in a plane identified by line 1212, FIGURE 7 and looking in the direction of the arrows;

FIGURE 13 is a longitudinal axial section of another and modified form of the invention;

FIGURE 14 is a transverse section to an enlarged 3,240,031 Patented Mar. 15, I966 scale, taken in a plane identified by line 14-14, FIG- URE 13;

FIGURE 15 is a longitudinal axial section taken in a plane shown by line 1515, FIGURE 13;

FIGURE 16 is a transverse section on line 1616 FIGURE 13;

FIGURE 17 shows the coupling sleeve in side elevation;

FIGURE 18 is an end view of the sleeve depicted upon FIGURE 17;

FIGURE 19 shows in detail, to a scale enlarged over FIGURE 13, one of the two connecting shafts used in the coupling;

FIGURE 20 is view corresponding to, and looking from the left of FIGURE 19;

FIGURE 21 is a view corresponding to, and looking down upon FIGURE 19; and

FIGURE 22 is a detail view to the same scale as FIGURES 19, 20 and 21, showing the end portion of the unit rollers with coupling removed, a part of the sleeve being broken away to show the construction and arrangement internally of the sleeve.

In drawing machines of the type involved, it is highly desirable for a uniform, high-quality product, that all portions of the lower drawing rollers operate at the same peripheral speed. Under such conditions, there results a superior high-quality yarn such as that depicted upon FIGURE 1(a), wherein successive transverse sections of the product are uniform and, as a secondary but highly desirable result, breakage or severance of the yarn is reduced to an absolute minimum.

However, when the lower roller Sections are rigidly connected there is a torsional oscillation from one end of the roller to the other, having a period of from 20 to 40 seconds, and a twist or torsion angle of from about 35 to 40 and which, under severe conditions, may be as great as 10. This torsional vibration results, in an obvious way, in variation of the instantaneous peripheral speeds of the interconnected sections of the roller and also a continuous variation in relative speeds of the several sections. As a result, the yarn produced has more or less uniformly-spaced nodules or enlargements as shown upon FIGURE 1(1)), which are undesirable because the resulting fabric is of inferior quality and appearance. Furthermore, in an equally obvious way, the aforesaid torsional vibration results in breakage, severance, fouling of rollers, and consequent loss of time due to the resulting necessary shutdown. When a machine of the type being described, having rigidly coupled roller sections, is operated at ultra-high speeds, the yarn produced has the equally undesirable form shown at FIGURE 1(0), wherein the nodules are simply of greater length and spacing, so that the resulting yarn is non-uniform and of poor quality.

When as frequently happens, the successive bearings of the lower roller are not properly and accurately aligned, or become out of line in use, the quality of the yarn is even more deleteriously affected due to the fact that the pressure between upper and lower rollers, at any given transverse section, varies as the lower roller vibrates up and down and thus accentuates the bunching depicted upon FIGURES 1(1)) and (c).

FIGURES 2 through 6 clearly illustrate, to an exaggerated scale how three consecutive lower roller bearings which are out of line, effect changes in pressure between the lower and upper roller sections. In practice due to faulty installation, or to non-uniform Wear of bearings, or uneven settling of the machine supports, it is found virtually impossible to maintain the axes of all roller bearings coaxial. If, for example, we consider any three consecutive lower roller bearings a, b, c, as in FIGURES 2 and 4, with bearing b at a greater elevation than bearing a, the difference in elevation which is denoted as x at bearing b, becomes 2x at bearing and if bearing c is brought into alignment with bearing a, while bearing 12 remains out of alignment, the resulting situation depicted at FIGURE 4 shows that for each rotation the roller must deflect at bearing 11 through a distance 2x. The same deleterious results are depicted at FIGURES 3 and when, of three bearings a, e, 1, bearing 2 is positioned below, or out of alignment with, bearing d, by the distance y. As in the preceding case bearing f would have to be out of line by the distance 2y for alignment of all three bearings; and if bearings d and f are properly aligned While bearing e retains its out-of-line position, the roller shaft must deflect at bearing e through the distance 2y, for each rotation thereof.

A typical installation of a lower roller is illustrated at FIGURE 6, where the out-of-line condition of several bearings is illustrated and, from a consideration of this figure, the numerous drawbacks inherent therein become clear, namely, (1) variation in pressure of any given roller section in dependence upon its rotational position, (2) torsional vibration caused in part by continuous changes in resistances to rotation of the out-ofline sections, (3) transverse vibrations due to synchronous changes in the radial forces effective on out-ofline bearings, (4) periodic variations in rotational or peripheral velocities of the successive roller sections caused by the previously-enumerated conditions.

The present invention obviates the aforesaid drawbacks of prior art drafting devices and produces a superior and high quality of yarn, eliminating the conditions just enumerated by obviating torsional vibration and assuring that each roller section rotates freely in its bearings, and maintains at all times constant pressure against the corresponding portions of the upper roller and with no variation in resistance to rotation.

FIGURES 7 through 12 depict a form of the invention wherein the contiguous ends of roller sections 80 and 80 are interconnected by a bearing sleeve 87, shown in detail upon FIGURES and 11. In this species the roller sections are all identical and reversible, end for end. Thus each section has axial bores 81, 81' opening through its ends. Confining attention to end 80 as shown upon FIGURE 8, bore 81 is enlarged between its ends as indicated at 90', to define an annular chamber 89 of greater diameter than bore 81'.

A short plain shaft section 82 has a press fit in bore 81. Its left end projects outwardly as indicated at 83'. Thus an annular space 84' is left between the shaft and counterbore 91.

The left and right halves of FIGURE 10 show coupling sleeve 87 in elevation and axial section, respectively, and from inspection of this figure, as well as of FIGURE 11, it is noted that each end of the sleeve is axially slotted to define four equal and equiangular spaced teeth or projections 86. Likewise that portion of bore 81 between its outer end and chamber 89 is cut away to define four axially extending splines 91' each sized and positioned to receive, with a loose fit, a corresponding one of teeth 86. Since the construction shown for roller section 80, at the left of FIGURE 7, is a duplicate of the one just described, it is suflicient to identify shaft section 82 having a press fit in axial bore 81 of the shaft, annular chamber 89, teeth 86 integral with the left end of bearing or coupling sleeve 87, and splines 91 in the end portion of bore 81.

The outer surface of sleeve 87 forms the inner race for a double roller bearing mounted in block 88. See FIGURE 7. As will be noted from this figure, the bearing consists of an outer race 88a held in place by cap 88b, and a cage 88d retaining a double row of rollers 882. End seals 88] and 88g each having a press fit within a respective end of the outer race, retain lubricant, which may be added through an opening closed by removable plug 88/1. The parts are dimensioned to leave a small clearance a, FIGURE 7, between confronting ends of shafts 82 and 82.

In the coupling just described each roller section and its shaft, may have a slight angular movement in planes through the axis of sleeve 87, as well as a slight angular movement about said axis relatively to the sleeve. Thus a slight eccentricity or out-of-line disposition of any one, or both, of two contiguous roller sections is fully compensated. When any bearing sleeve 87 becomes worn, it can be replaced, so that the rollers themselves can be used indefinitely.

Referring to FIGURES 13 to 22, there is shown a modified form of the invention as just described in connection with FIGURES 7 through 12, wherein, referring particularly to FIGURES l7 and 18, bearing sleeve 108 has a central cylindrical portion 107. Each end of the sleeve is externally tapered slightly, and cut away as at 106, at two diametrically opposite locations to define a pair of axial projections having a common internal axial bore surface with central portion 107. A radial hole 110 permits escape of air when the ends 97 of the shafts of the roller section are thrust into the sleeve.

Confining attention to the left roller section 95 as viewed at FIGURE 37 and as shown to an enlarged scale at FIGURES 14 and 15, each end is axially bored at 96 to provide a cylindrical surface enlarged at its inner end as shown. The outer end of the bore is counterbored at 101 and between these bores there is an enlargement 102 to receive an adjusting ring 103.

One of the duplicate shafts is shown in detail at FIG- URES 19, 20 and 21, and from these it is noted that each is machined to provide an end section 93 sized for a press fit Within bore 96, and when assembled, projecting slightly into enlargement 102. A key 99, FIGURES 13, 16 and 22, fits mating channels such as 94 in the wall of bore 96 and in section 93, to cause the roller section and shaft to rotate as a unit. Next in order, the shaft is provided with an intermediate section having flats 92 at diametrically opposite sides, so that this portion has a loose fit within the cut away portion 106 in the corresponding end of sleeve 108. The fit is such that the roller section may have a slight axial and rotational freedom with respect to the sleeve.

Following the flattecl section, the shaft terminates in an end cylindrical section 97 having a smooth fit within the sleeve.

In the assembly as shown at FIGURE 30, each roller section has freedom for limited angular movement in planes through the longitudinal axis of sleeve 108. Also due to the loose coupling between the flats 92 and the projections at the respective ends of the sleeve, each roller section has freedom for limited rotation relatively to the sleeve. The construction and arrangement are such that the roller sections of the entire length of one line can be set accurately. All parts are interchangeable and there is no bending when assembling or disassembling a line. Since all bearing sleeves 108 are interchangeable these can be replaced as required, while the roller sections themselves may be used indefinitely.

The operation will be clear from the foregoing description, drawings and appended claims.

The specification describes examples only of the invention for the purposes here disclosed. It is however, intended to cover all changes and modifications of the embodiments shown, and all combinations of the present invention with conventional elements, which do not depart from the spirit and scope of the invention as claimed.

Having now fully disclosed the invention, what I claim and desire to secure by Letters Patent is:

1. In a textile drawing mechanism, a drawing roll comprising a pair of roller sections each having splined coaxial bores extending inwardly from its respective ends, a one-piece connector sleeve having a central bearing portion and first and second splined portions extending from respective ends of said central bearing portion, all said portions being coaxial, each said splined portion having a smooth fit within the splined bore of a respective one of said roller sections, the splined portions at each end of said sleeve having a circumferential dimension less than the corresponding dimension of the splines of said bores, whereby said sections are positively interconnected in axially-spaced relation for rotation, while having limited relative rotation about their common axis, a bearing block mounted between said roller sections, and an antifriction bearing mounted in said bearing block, said connector sleeve forming the inner race of said bearing.

2. In a textile drawing mechanism, a drawing roll comprising a pair of roller sections each having splined coaxial bores extending inwardly from contiguous ends of said sections, a bearing, and a one-piece connector sleeve having a cylindrical central bearing portion and first and second splined extensions projecting from the respective ends of said central bearing portion, exteriorly of said bearing, each said splined extension loosely fitting the splined bore of a respective one of said roller sections, each spline of each said extension having a circumferential dimension less than the spline channels of said bores, whereby said sections are positively interconnected in axially-spaced relation for rotation while having limited relative rotation about their common axis, a bearing block mounted between said roller sections, and an anti-friction bearing mounted in said bearing block, said connector sleeve forming the inner race of said bearing.

3. In a textile drawing mechanism, first and second roller sections each having first and second plain bores extending axially inwardly from its respective ends, each said bore having a splined counterbore opening through its outer end, a bearing sleeve having splined ends each fitting the splined counterbore of a respective one of said roller sections and connecting said sections in axiallyspaced coaxial relation for rotation as a unit, a bearing journaling said sleeve for rotation about the common axis of said sections and sleeve, the splines of said sleeve having a circumferential dimension less than the corresponding dimension of the splines of said bores, to permit limited relative rotation between said sections, and first and second plain shafts each having one end tightly fitting the bore of a respective roller section and its other end projecting into and fitting the corresponding end of said sleeve, the contiguous ends of said plain shafts being axially spaced within said sleeve.

References Cited by the Examiner UNITED STATES PATENTS 854,715 5/1907 Gallan et al 64--15 1,684,919 9/1928 Keyser 64-6 2,389,581 11/1945 Tarr 641 2,630,341 3/1953 Downey 64-1 2,775,104 12/1956 Karcher 641 2,844,011 7/1958 Meier 64-1 2,976,702 3/1961 Pietsch 64-1 FOREIGN PATENTS 943,455 5/1956 Germany.

MILTON KAUFMAN, Primary Examiner,

FRANK R. SUSKO, ROBERT C. RIORDON, Examiners. 

1. IN A TEXTILE DRAWING MECHANISM, A DRAWING ROLL COMPRISING A PAIR OF ROLLER SECTIONS EACH HAVING SPLINED COAXIAL BORES EXTENDING INWARDLY FROM ITS RESPECTIVE ENDS, A ONE-PIECE CONNECTOR SLEEVE HAVING A CENTRAL BEARING PORTION AND FIRST AND SECOND SPLINED PORTIONS EXTENDING FROM RESPECTIVE ENDS OF SAID CENTRAL BEARING PORTION, ALL SAID PORTIONS BEING COAXIAL, EACH SAID SPLINED PORTION HAVING A SMOOTH FIT WITHIN THE SPLINED BORE OF A RESPECTIVE ONE OF SAID ROLLER SECTIONS, THE SPLINED PORTIONS AT EACH END OF SAID SLEEVE HAVING A CIRCUMFERENTIAL DIMENSION LESS THAN THE CORRESPONDING DIMENSION OF THE SPLINES OF SAID BORES, WHEREBY SAID SECTIONS ARE POSITIVELY INTERCONNECTED IN AXIALLY-SPACED RELATION FOR ROTATION, WHILE HAVING LIMITED RELATIVE ROTATION ABOUT THEIR COMMON AXIS, A BEARING BLOCK MOUNTED BETWEEN SAID ROLLER SECTIONS, AND AN ANTIFRICTION BEARING MOUNTED IN SAID BEARING BLOCK, SAID CONNECTOR SLEEVE FORMING THE INNER RACE OF SAID BEARING. 